System for controlled fluid heating using air conditioning waste heat

ABSTRACT

A system is disclosed which utilizes air conditioning waste to heat a second fluid such as swimming pool water. The second condenser for pool water heating is connected in parallel with the air conditioning condenser. An accumulator is connected between the condensers and the expansion valve to absorb fluctuations in refrigerant level due to different operating conditions caused by the pool water heating, thereby ensuring that liquid refrigerant is always supplied to the expansion valve. A controller reads the ambient air temperature at the air conditioning condenser and reads the air conditioning system condensing pressure and uses an algorithm to compute ambient air fan speed at the air conditioning condenser based on these two inputs to maintain a consistent heated pool water temperature. 
     An alternate system includes first and second condensers connected in series with an accumulator connected between the second condenser and the expansion valve and a pressure equalization line connected between the compressor and the accumulator. A controller reads the ambient air temperature at the air conditioning condenser and reads the air conditioning system condensing pressure and uses an algorithm to compute ambient air fan speed at the air conditioning condenser based on these two inputs to maintain a consistent heated pool water temperature.

TECHNICAL FIELD

The present invention relates to the recovery of waste heat from arefrigeration or an air conditioning system, to provide a heated fluidat a controlled, consistent temperature.

BACKGROUND

The use of a heater to warm swimming pool water is quite common amongswimming pool owners. Many existing systems use electric, gas, or fueloil-heating units, which are costly to operate. Attempts to utilize airconditioning waste heat to provide a safe, economical, and low energyconsuming pool water heating system, such as shown in U.S. Pat. No.3,976,123 issued to Davies, have not been commercially successful asprevious systems did not maintain a constant discharge temperature, wereinefficient to operate, and could cause equipment damage.

SUMMARY OF THE INVENTION

It is a general object of the present invention to provide a pool waterheater that uses the waste heat from a refrigeration or an airconditioning system to heat pool water, or other fluids, to useful anddesired temperatures, and to do such water heating with consistent,controlled output water temperatures, with optimum air conditioningsystem efficiency, and without equipment damage.

This and other objects and features are provided, in accordance with oneaspect of the present invention, by an air conditioning systemcomprising a compressor connected to a first condenser and to a secondcondenser, connected in parallel or in series. The condensers and thecompressor are connected to an accumulator, the accumulator connected toan expansion valve, the expansion valve connected to an evaporator, andthe evaporator connected to the compressor. A pump draws water from apool of water and supplies the water to the first condenser and then thewater is returned to the pool. A control system adjusts the thermalperformance of the second condenser to increase or decrease thecondensing pressure and condensing temperature to heat the water to thedesired temperature, based on the readings of two sensors, pressureand/or temperature, while the accumulator supplies the proper amount ofliquid refrigerant to the expansion valve during all phases ofoperation. Other applications are presented for hot water heating andclothes drying.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1A shows a prior art air conditioning waste heat recovery systemfor heating pool water; FIG. 1B, 1C, and 1D show a partial enlargementof FIG. 1A and show the condition of the hot high temperature gaseousand liquid refrigerant with no pool water heating, partial pool waterheating with the system charged with no pool water heating, and partialpool water heating with system charged with full pool water heating,respectively;

FIG. 1E shows Theoretical Outlet Water Temperature, Air ConditioningSystem Condensing Pressure, Condenser Fan ON/OFF, and Hot WaterRequirements at various Operational Conditions;

FIG. 2A shows a first embodiment of the present invention airconditioning waste heat recovery system for heating pool water where thecondensers are connected in series to an accumulator with a pressureequalization line between the compressor and accumulator, and thethermal performance of refrigerant-to-air condenser is controlled byadjusting its fan speed; FIG. 2B, 2C, and 2D show a partial enlargementof FIG. 2A, and show the condition of the hot high temperature gaseousand liquid refrigerant with no pool water heating, partial pool waterheating, and maximum pool water heating, respectively;

FIG. 3A shows a second embodiment of the present invention airconditioning waste heat recovery system for heating pool water Where thecondensers are connected in parallel between the compressor andaccumulator and the thermal performance of refrigerant-to-air condenseris controlled by adjusting its fan speed; FIG. 3B, 3C, and 3D show apartial enlargement of FIG. 3A, and show the condition of the hot hightemperature gaseous and liquid refrigerant with no pool water heating,partial pool water heating, and maximum pool water heating,respectively;

FIG. 3E is similar as FIG. 3A except the pool water heater is replacedby domestic or commercial hot water heating;

FIG. 3F is similar as FIG. 3A except the pool water heater is replacedby clothes dryer heating;

FIG. 4A and 4B show the control graphs for controlling the watertemperature from the refrigerant-to-water condenser using ambient airtemperature at the refrigerant-to-air condenser and exit watertemperature at the refrigerant-to-water condenser to modulate fan motorspeed in FIG. 2A and 3A and associated Figures;

FIG. 5A and 5B show the control graphs for controlling the watertemperature from the refrigerant-to-water condenser using ambient airtemperature at the refrigerant-to-air condenser and the systemcondensing pressure to modulate fan motor speed in FIG. 2A and 3A andassociated Figures;

FIG. 6A shows Theoretical Outlet Water Temperature, Air ConditioningSystem Condensing Pressure, Condenser Fan Speed, and Hot WaterRequirements at various Operational Conditions.

DETAILED DESCRIPTION

The use of air conditioning waste heat to heat swimming pool water hasbeen demonstrated and is well know in the art. Davies discloses a systemfor controlled heating of pool water using waste heat of an airconditioner where the refrigerant-to-air condenser fan is cycled on andoff in response to a sensor monitoring the temperature of the waterexiting the refrigerant-to-water condenser. If the water temperature isbelow the Fan Off Set Point, the air conditioning condenser fan will beturned off, increasing the condensing pressure and temperature,increasing the amount of heat going into the refrigerant-to-watercondenser, increasing the temperature of the water exitingrefrigerant-to-water condenser. When the water temperature reaches theFan On Set Point, which is higher than the Fan Off Set Point, the airconditioning fan will be turned on, decreasing the condensing pressureand temperature, reducing the amount of heat going into therefrigerant-to-water condenser, lowering the temperature of the waterexiting refrigerant-to-water condenser. However, there are a number ofinherent disadvantages present in this and other prior art systems. Thecycling of the condenser fan is a poor practice as the rate of cyclingcan become too high, burning out the condenser fan motor. Cycling of thecondenser fan increases as the water heating BTU/hr load decreases aswhen the inlet water temperature approaches the Fan Off Set Point.Increasing the temperature separation between the Condenser Fan On andOff Set Points will reduce the instances of motor burn out but increasesthe temperature swing in the outlet temperature of the water exiting therefrigerant-to-water condenser which is unacceptable in manyapplications like domestic hot water heating.

Davies states “In operation, the transfer of heat to the pool water doesnot interfere with the refrigeration and cooling capabilities ofrefrigeration loop”. This is a common false belief, because it isassumed that the air conditioning system is more efficient due to theadditional condensing capacity of the refrigerant-to-water condenser.But in fact, a 15% degradation has been observed with a small, 1-tonpool water refrigerant-to-water condenser installed on a 3-ton airconditioning system. The degradation is caused by therefrigerant-to-water condenser, which when in operation takes liquidrefrigerant from the refrigerant-to-air condenser, disrupting thebalance of liquid refrigerant in the system, allowing hot gaseousrefrigerant to reach the air conditioner's expansion valve andevaporator. Larger degradations will occur if largerrefrigerant-to-water condensers are used, which is one reason why priorair pool water heaters use smaller refrigerant-to-water condensers. Theair conditioning system is usually charged with refrigerant without poolwater heating. With just the refrigerant-to-air condenser running,refrigerant is added until a solid column of liquid exits therefrigerant-to-air condenser. The solid column of refrigerant liquid canbe seen in a sight glass installed after the condenser and the solidcolumn of refrigerant liquid keeps high pressure gaseous refrigerant outof the evaporator, which would degrade the operation of the evaporator.When the pool water is turned on, refrigerant is condensed in therefrigerant to-water condenser and this amount of liquid is removed fromthe refrigerant-to-air condenser allowing high pressure gaseousrefrigerant to reach the expansion valve and evaporator. Gaseousrefrigerant will now be seen in the sight glass. The result is theoperational efficiency of the air conditioning system is lowered. Theamount of gaseous refrigerant reaching the expansion valve andevaporator is dependent upon the amount of refrigerant being condensedin the refrigerant-to-water condenser. Charging the air conditioner whenthe pool heater is running will keep the refrigerant liquid column up tothe expansion valve and evaporator while water is being heated by therefrigerant-to-water condenser. But when the pool heater is turned offexcess liquid refrigerant will pass thru the evaporator to thecompressor, destroying the compressor, as the compressor cannot compressa liquid. A larger pool water refrigerant-to-water condenser willincrease the risk of compressor damage, which is why they are sized tothe small side. Air conditioning inefficiency due to high pressuregaseous refrigerant reaching the evaporator and compressor damage risksare additional problems that have limited the use of air conditioningwaste heat to heat pool water or other fluids.

Referring now to FIG. 1A, a prior art air conditioning waste heatrecovery system for heating pool water is shown generally as 100. Theair conditioning waste heat recovery system comprises a compressor 101,a pool water condenser 102, a refrigerant-to-air condenser 103, anexpansion valve 104, an air to refrigerant evaporator 105 andrefrigerant-to-air fan motor controller 108. The refrigerant flow isshown by arrows 110. Compressor 101 is connected to and supplies gaseoushigh pressure refrigerant-to-water condenser 134 condensing line 114with refrigerant line 112, the refrigerant-to-water condenser 134condensing line 114 is connected to and supplies high pressure gaseousand/or liquid refrigerant to refrigerant-to-air condenser 103refrigerant line 118 with refrigerant line 116, the refrigerant-to-aircondenser 103 refrigerant line 118 supplies high pressure liquidrefrigerant to expansion valve 104 with refrigerant line 121, theexpansion valve 104 supplies low pressure liquid refrigerant toevaporator 105 refrigerant line 124, the evaporator 105 refrigerant line124 supplies low pressure gaseous refrigerant to compressor 101 withrefrigerant line 128. The pool water flow is shown by arrows 130. Pump131 is connected to and draws pool water 138 from pool 137 with line139, pump 131 is connected to and supplies the pool water 138 to therefrigerant-to-water condenser 134 with water line 132, the watercondenser 134 puts pool water 138 in contact for heat exchange withrefrigerant line 114 which heats the pool water 138, the water condenser134 supplies heated water to the pool 137 with water line 136. The wasteheat recovery system refrigerant-to-air condenser 103 consists of arefrigerant line 118 with thermally connected fins 164, fan motor 160with fan blades 166 that blow ambient air 162 across the fins 164,heating the ambient air 162. The waste heat recovery system expansionvalve 104 causes the high pressure liquid refrigerant to become lowpressure liquid refrigerant. The waste heat recovery system air torefrigerant evaporator 105 consists of a refrigerant line 124 withthermally connected fins 184, fan motor 180 with fan blades 186 whichblow interior home air 182 across fins 184, cooling the interior homeair 186, supplying low pressure gaseous refrigerant 141 to compressor201. Refrigerant-to-air fan motor controller 108 reads the temperatureof the exit water at sensor 175 with electrical line 173 and turns fanmotor 160 off once the predefined exit water temperature is reached withelectrical line 171. Now, all of the condensing must happen at therefrigerant-to-water condenser 134 refrigerant line 114 which increasesthe condensing pressure and temperature, heating the pool water 138 to ahigher temperature. Fan motor controller 108 continues to read the exitwater temperature with sensor 175 and will turn fan motor 160 back onwhen the exit water temperature increases to the predefined Fan ONtemperature. Condensing will now occur in both condensers, lowering thecondensing pressure and temperature, heating the pool water 138 to alower temperature. If the pool water 138 temperature drops below thepredefined Fan OFF set point, the OFF/ON cycle will repeat. The in homethermostat 172 tells fan motor controller 108 when system 100 isrunning.

Referring now to FIG. 1B, 1C, and 1D, partial enlargements of FIG. 1A,where refrigerant lines 112, 114, 116, 118, and 121 are shown coming to,through, and exiting pool water and refrigerant-to-air condenser 103 atvarious operational conditions. Refrigerant flow direction is shown byarrows 110.

Referring now to FIG. 1B where the pool water condenser is not beingused and there is no pool water flow. Only the refrigerant-to-aircondenser 103 is in operation and it is supporting the full airconditioning load. Liquid refrigerant 144 is only condensed in therefrigerant-to-air condenser 103. Condensing starts at point 118 a whenthe gaseous high pressure, high temperature refrigerant 141 comes incontact for heat exchange with the portion of refrigerant line 118 thatis in contact for heat exchange with the thermally conductive fins 164that are cooled by ambient air 162. Condensing basically ends at point118 b as refrigerant line 118 continues past thermally conductive fins164. Approximately one half of the condenser volume between point's 118a and 118 b are filled with liquid refrigerant 144. The air conditioningsystem is normally charged with refrigerant with just the refrigerationto air condenser running, and charging is stopped when the outlet of therefrigerant-to-air condenser is solid liquid as seen in sight glass 119.

Referring now to FIG. 1C, where both the pool water condenser 102 andrefrigerant-to-air condenser 103 are in operation. Pool water flow isshown by arrows 130. Liquid refrigerant 144 is condensed in bothcondensers. Condensing starts at point 114 a when the gaseous highpressure, high temperature refrigerant comes in contact for heatexchange with the portion of refrigerant line 114 that is in contact forheat exchange with and cooled by pool water 138. Now there is liquidrefrigerant in both condensers and since the system was charged withonly the refrigeration to air condenser 103 running, there is not enoughrefrigerant in the system to allow a solid column of liquid exiting therefrigerant-to-air condenser 103 as seen in sight glass 119. Now bothgaseous high pressure refrigerant 141 and liquid refrigerant 144 reachthe expansion valve 104 and air to refrigerant evaporator 105, reducingsystem efficiency

Referring now to FIG. 1D, where the air conditioning system has beencharged with both the pool water condenser 102 and therefrigerant-to-air condenser 103 running. Now there is a solid column ofliquid refrigerant 144 exiting the refrigerant-to-water condenser 134and there is no high pressure gas 141 reaching the expansion valve 104or the air to refrigerant evaporator 105, as shown in sight glass 119,for proper operational efficiency. However, when the pool water isturned off, the refrigerant liquid volume will revert to that of FIG. 1Band the liquid refrigerant volume difference between FIG. 1D and FIG. 1Bwill go into the air to refrigerant evaporator 105 and on to thecompressor 101. Any liquid refrigerant 144 reaching the compressor 101will cause severe damage and is dangerous.

Referring now to FIG. 1E, where theoretical Outlet Water Temperature,Air Conditioning System Condensing Pressure, Condenser Fan ON/OFF, andHot Water Requirements at various Operational Conditions are shown forFIG. 1A. Five Operational Conditions are presented. The No. 1 Conditionis for no pool water heating and the Hot Water requirement is zero. Theair conditioning system is working normally as shown is FIG. 1B. The No.5 Condition is for full pool water heating and the Hot Water requirementis 100%. Refrigerant condensing is taking place only in therefrigerant-to-water condenser. There is very little cycling of fanmotor 160 under this condition and if the system was charged withrefrigerant under this operating condition, the liquid refrigerantdistribution would be as shown in FIG. 1D. If the system was chargedwith refrigerant under operation condition No. 1, the liquid refrigerantdistribution would be as shown in FIG. 1C and hot gaseous refrigerantwould reach the expansion valve, degrading air conditioning performance.The No. 2, No. 3, and No. 4 conditions are for 25%, 50% and 75% HotWater requirements. Fan motor cycling decreases as the Hot Waterrequirements increase. Fan motor cycling at the lower Hot Waterrequirements will damage the typical refrigerant-to-air condenser fanmotor. Fan motor cycling can be reduced by increasing the differencebetween the Fan ON and Fan OFF set points but this causes higher hotwater temperature differences between Fan ON and Fan OFF operation,which is unacceptable to other applications like hot water heating. Ifthe system was charged with refrigerant under operating condition No 5,the liquid refrigerant distribution would be as shown in FIG. 1E, butexcess liquid refrigerant, the liquid difference between FIG. 1D and 1E,would be available to damage the compressor. Under these conditions, thelower the hot water requirements, the more liquid refrigerant isavailable to damage the compressor. If the system was charged withrefrigerant under operation condition No. 1, the liquid refrigerantdistribution would be as shown in FIG. 1C and hot gaseous refrigerantwould reach the expansion valve, degrading air conditioning performance.If the system is charged under conditions 2, 3, or 4, the system willonly operate correctly at these specific operating conditions.

Accordingly, it is desirable to have an air conditioning waste heatsystem capable of heating pool water to desired temperatures with goodoperational efficiency, consistent output temperatures, and no equipmentdamage.

Referring now to FIG. 2A, an air conditioning waste heat recovery systemfor heating pool water according to the present invention is showngenerally as 200, and comprises a compressor 201, a pool water condenser202, a refrigerant-to-air condenser 203 where the condensers areconnected in series; a pressure equalization line 206, an accumulator207, a fan speed control 208 for the refrigerant-to-air condenser 203fan motor 260, an expansion valve 204, and an air to refrigerantevaporator 205. Arrows 210 show the refrigeration flow. Compressor 201is connected to and supplies gaseous high pressure refrigerant torefrigerant line tee 215 with refrigerant line 213, the refrigerationtee 215 is connected to and supplies gaseous high pressure, hightemperature refrigerant to refrigerant-to-water condenser 234 condensingline 214 with refrigerant line 212, the refrigerant-to-water condenser234 condensing line 214 is connected to and supplies gaseous and orliquid refrigerant-to-air condenser 203 refrigerant line 218 withrefrigerant line 216, the refrigerant-to-air condenser 203 refrigerantline 218 supplies high pressure liquid refrigerant to accumulator 207with refrigerant line 220. The tee 215 also supplies gaseous highpressure refrigerant to accumulator 207 with pressure equalization line206. The accumulator 207 is connected to and supplies high pressureliquid refrigerant to expansion valve 204 with refrigerant line 221, theexpansion valve 204 supplies low pressure liquid refrigerant toevaporator 205 refrigerant line 224, the evaporator 205 refrigerant line224 supplies low pressure gaseous refrigerant to the compressor 201 withrefrigerant line 228. The pool water condenser 202 water flow is shownby arrows 230. Pump 231 is connected to and draws pool water 238 frompool 237 with line 239, the pump 231 is connected to and supplies thepool water 238 to the refrigerant-to-water condenser 234 with water line232, the water condenser 234 puts the pool water 238 in contact for heatexchange with the refrigerant line 214 which heats the pool water 238,the water condenser 234 supplies heated pool water 238 to the pool 237with water line 236. The waste heat recovery system refrigerant-to-aircondenser 203 consists of a refrigerant line 218 with thermallyconnected fins 264, fan motor 260 with fan blades 266 that blow ambientair 262 across the fins 264, heating the ambient air 262. Fan speedcontroller 208 is connected to and adjusts fan motor 260 speed from zeroto 100%, which controls the amount of condensation taking place in therefrigerant-to-air condenser 203 and raises or lowers the condensingpressure in both condensers to obtain the desired water temperatureexiting the refrigerant-to-water condenser 234. The waste heat recoverysystem expansion valve 204 causes the high pressure liquid refrigerantto become low pressure liquid refrigerant. The waste heat recoverysystem air to refrigerant evaporator 205 consists of a refrigerant line224 with thermally connected fins 284, fan motor 280 with fan blades 286which blow interior home air 282 across the fins 284, cooling theinterior home air 286 and supplying gaseous refrigerating to compressor201 by refrigerant line 228. The control system 208 that modulates therefrigerant-to-air condenser 203 fan 206 will be discussed in detaillater.

Referring now to FIG. 2B, 2C, 2D, partial enlargements of FIG. 2A, whererefrigerant lines 213, 212, 214, 215, 216, 218, and 221 are shown comingto, through, and exiting pool water condenser 202, refrigerant-to-aircondenser 203 and accumulator 207; and pressure equalization line 206 isconnected between tee 215 a head of pool water refrigerant-to-watercondenser 202 and the accumulator 207. Arrows 210 show refrigerant flowdirection.

Referring now to FIG. 2B, the pool water condenser 202 is not being usedand there is no pool water flow. The refrigerant-to-air condenser 203 isin operation and its condensing capacity is controlled by fan motorcontroller 208 running fan motor 280 at 100 percent of fan capacity,because water heating is not desired. Liquid refrigerant 244 iscondensed only in the refrigerant-to-air condenser 203. Condensingstarts at point 218 a when the gaseous high pressure, high temperaturerefrigerant 241 comes in contact for heat exchange with the portion ofrefrigerant line 218 that is in contact for heat exchange with thecooling fins 264. Condensing basically ends at point 218 b asrefrigerant line 218 continues past thermally conductive fins 264. Thecondensing volume between point's 218 a and 218 b are approximately onehalf filled with liquid refrigerant. The air conditioning system hasbeen charged with the refrigerant with just the pool water condenser 202running as shown in FIG. 2D, which is the maximum liquid refrigerantcondition and charging, stopped when the outlet of therefrigerant-to-air condenser 203 is solid liquid as seen in sight glass119. The accumulator 207 has the capacity to receive the unneeded liquidrefrigerant when the pool water condenser is not in operation andpressure equalization line 206 allows accumulator volume changes withoutforcing the excess liquid refrigerant through the system, to avoidcompressor damage.

Referring now to FIG. 2C, where both the pool water condenser 202 andrefrigerant-to-air condenser 203 are both in operation. Arrows 230 showpool water flow. Condensing starts at point 214 a when the gaseous highpressure, high temperature refrigerant 241 comes in contact for heatexchange with the portion of refrigerant line 214 that is in contact forheat exchange with and cooled by the pool water 238. Now there is liquidrefrigerant in both condensers and since the system was charged withonly the pool water condenser 202 running, there is enough liquidrefrigerant 244 in the accumulator 207 to supply liquid refrigerant 244so that a continuous column of liquid exits the accumulator 207 as seenin sight glass 219. Now only liquid refrigerant 244 reaches theexpansion valve 204 and air to refrigerant evaporator 205, maintainingsystem efficiency. Fan motor controller 208 adjusts fan motor 260 speedbetween zero and 100%, which increases or decreases the condensingpressure and temperature to maintain the desired water temperature atthe point 214 b in the pool water refrigerant-to-water condenser 202.

Referring now to FIG. 2D, where the pool water condenser 202 is runningat 100% and carrying the full air conditioning load. Refrigerant-to-aircondenser 203 fan motor 280 has been turned off by motor controller 208.This is the maximum water heating capability of the waste heat recoverysystem 200 and all of the condensing energy is going into heating thepool water. Arrows 230 show pool water flow. Condensing starts at point214 a when the gaseous high pressure, high temperature refrigerant 241comes in contact for heat exchange with that portion of refrigerant line214 that is in contact for heat exchange with and cooled by the poolwater 238. Now there is the maximum liquid refrigerant in bothcondensers and this is the operational condition for proper charging ofthe air conditioning waste heat recovery system for heating pool water.Now there is enough liquid refrigerant 244 in the accumulator 207 tosupply liquid refrigerant 244 to allow a solid column of liquid to exitthe accumulator 207 when pool water condenser 202 is not in operationand there is enough accumulator capacity to accept unneeded liquidrefrigerant when pool water condenser 202 is running up to 100% ofcapacity. Since the accumulator maintains a constant liquid refrigerantsupply to expansion valve 204 and the accumulator has the capacity tohold unneeded liquid refrigerant 244, the system works at peakefficiency and there is no risk of compressor damage.

Referring now to FIG. 2A again, fan 260 controller 208 receives inputsor sends outputs from water exit temperature sensor 275 by electricalline 273, from condensing pressure sensor 277 at accumulator 207 byelectrical line 278, from ambient air temperature sensor 276 atrefrigerant-to-air condenser 203 by electrical line 272, and controlsfan motor 260 speed with control line 271. Controller 208 determines ifwater heating is needed and controller 208 turns on the air conditioningsystem by electrical line 274 to in home thermostat 272. Controller thenadjusts the speed of fan 260 per control graphs shown in FIG. 4A and 4Bto maintain the selected water exit temperature fromrefrigerant-to-water condenser 234 as read at sensor 275.

The size of the accumulator is dependent upon the sizes of the systemcondensers 234 and 203. Typically the accumulator volume must be atleast equal to the volume delta between the liquid volume shown in FIG.2B and the liquid volume shown in FIG. 2D between point 214 a and thepoint where line 221 enters accumulator 207. This will guarantee thatthe expansion valve only sees liquid refrigerant under all statedoperating conditions. A 5 to 10% additional accumulator volume isusually added as a safety factor.

Referring now to FIG. 3A, an air conditioning waste heat recovery systemfor heating pool water accordingly to the present invention is showngenerally as 300 where the condensers are connected in parallel and therefrigerant-to-air condenser capacity is controlled by ambient air flow362. The assembly 300 comprises a compressor 301, a pool water condenser302, a refrigerant-to-air condenser 303, an accumulator 307, a fan speedcontrol 308 for the refrigerant-to-air condenser 303, an expansion valve304, and an air to refrigerant evaporator 305. Arrows 310 show therefrigeration flow. Compressor 301 is connected to and supplies gaseoushigh pressure refrigerant to refrigerant line tee 315 with refrigerantline 313, the refrigeration tee 315 is connected in parallel to andsupplies gaseous high pressure refrigerant to both refrigerant-to-watercondenser 334 condensing line 314 with refrigerant line 312, andrefrigerant-to-air condenser 303 condensing line 318 with refrigerantline 316. Both condensers supply high pressure gaseous and/or liquidrefrigerant to accumulator 307 with refrigerant lines 317 and 320.Accumulator 307 supplies liquid refrigerant to expansion valve 305 andevaporator 304 with refrigerant line 321. Evaporator 304 supplies lowpressure gaseous refrigerant to compressor 301 with refrigerant line328. The pool water condenser 302 water flow is shown by arrows 330.Pump 331 is connected to and draws pool water 338 from pool 337 withline 339, the pump 331 is connected to and supplies the pool water 338to the refrigerant-to-water condenser 334 with water line 332, therefrigerant-to-water condenser 334 puts the pool water 338 in contactfor heat exchange with the refrigerant line 314 which heats the poolwater 338, the refrigerant-to-water condenser 334 supplies heated waterto the pool 337 with water line 336. The waste heat recovery systemrefrigerant-to-air condenser 303 consists of a refrigerant line 318 withthermally connected fins 364, fan motor 360 with fan blades 366 thatblow ambient air 362 across the fins 364, heating the ambient air 362and fan speed controller 308 which controls the amount of condensationtaking place in the refrigerant-to-air condenser 303 by adjusting theamount of ambient air 362 blowing over the fins 364. The waste heatrecovery system expansion valve 304 and air to refrigerant evaporator305 operate in the conventional manner supplying low pressure gaseousrefrigerating to compressor 301 by refrigerant line 328.

Referring now to FIG. 3B, 3C, and 3D, partial enlargements of FIG. 3A,where refrigerant lines 315, 313, 312, 314, 317, 316, 318, 320 and 321are shown coming to, through, and exiting pool water condenser 302,refrigerant-to-air condenser 303 and accumulator 307. Both condensersare connected in parallel. Refrigerant flow is show with arrows 310.

Referring now to FIG. 3B, pool water condenser 302 is not in operationand all condensing is occurring at the refrigerant-to-air condenser.Compressor 301 is connected to and supplies gaseous high pressurerefrigerant 341 to refrigerant line tee 315 with refrigerant line 313,the refrigeration tee 315 is connected in parallel to and suppliesgaseous high pressure refrigerant 341 to both refrigerant-to-watercondenser 334 condensing line 314 with refrigerant line 312, andrefrigerant-to-air condenser 303 condensing line 318 with refrigerantline 316. Both condensers supply high pressure gaseous 341 and liquidrefrigerant 344 to accumulator 307 with refrigerant line 317 and 320,respectively. Accumulator 307 supplies liquid refrigerant 344 toexpansion valve 305 and evaporator 304 with refrigerant line 321. Thepool water condenser 302 is not being used and there is no pool waterflow. The refrigerant-to-air condenser 303 is in operation and itscondensing capacity is controlled by fan motor controller 308 runningfan motor 360 at 100 percent of fan capacity. Liquid refrigerant 344 iscondensed only in the refrigerant-to-air condenser 303. Condensingstarts at point 318 a when the gaseous high pressure, high temperaturerefrigerant 341 comes in contact for heat exchange with the portion ofrefrigerant line 318 that is in contact for heat exchange with thecooling fins 364. Condensing basically ends at point 318 b asrefrigerant line 318 continues past thermally conductive fins 364.Accumulator 307 accepts or supplies liquid refrigerant 344 as required,maintaining a constant liquid refrigerant flow to expansion valve 304 asshown in sight glass 319.

Referring now to FIG. 3C, where both the pool water condenser 302 andrefrigerant-to-air condenser 303 are both in operation. Arrows 330 showpool water flow. Condensing starts at point 314 a when the gaseous highpressure, high temperature refrigerant comes in contact for heatexchange with the portion of refrigerant line 314 that is in contact forheat exchange with and cooled by the pool water 338. Now there is liquidrefrigerant in both condensers and since the system was charged withonly the larger volume condenser running, there is enough liquidrefrigerant 344 in the accumulator 307 to allow a solid column of liquidto exit the accumulator 307 as seen in sight glass 319. Now only liquidrefrigerant 344 reaches the expansion valve 304 and air to refrigerantevaporator 305, maintaining system efficiency. Fan motor controller 308adjusts fan motor 380 speed between zero and 100%, which increases ordecreases the condensing pressure and condensing temperature to maintainthe desired water temperature at the point 314 b in the pool watercondenser 302.

Referring now to FIG. 3D where only the pool water condenser 302 isrunning. Arrows 330 show pool water flow and refrigerant low is shown byarrows 310. Condensing starts at point 314 a when the gaseous highpressure, high temperature refrigerant comes in contact for heatexchange with the portion of refrigerant line 314 that is in contact forheat exchange with and cooled by the pool water 338. Fan motorcontroller 308 running fan motor 280 at zero percent of fan capacity,which makes all condensing take place in the pool water condenser 302.This is the maximum water heating condition. Accumulator 307 accepts orsupplies liquid refrigerant as required, maintaining a constant liquidrefrigerant flow to expansion valve 304 as shown in sight glass 319.

Referring now to FIG. 3E, which is similar to FIG. 3A except the poolwater source has been replaced with a hot water heater. Fan 360controller 308 receives inputs or sends outputs from water exittemperature sensor 375 by electrical line 373, from refrigerant-to-watercondenser 334, from water heater control module 381E by electrical line379E, from condensing sensor 377 at accumulator 307 by electrical line378, from ambient air temperature sensor 376 at refrigerant-to-aircondenser 303 by electrical line 372, and controls fan motor 360 speedwith control line 371. Water heater control module 381 tells controller308 that water heating is needed and the air conditioning system isturned on by electrical line 374 to in home thermostat 372. Controllerthen adjusts the speed of fan 360 per control graphs shown in FIG. 4Aand 4B or FIG. 5A and 5B to maintaining the selected water exittemperature from refrigerant-to-water condenser 334 as read at sensor375 or 377.

Referring now to FIG. 3F, which is similar to FIG. 3A except the poolwater source has been replaced with a clothes dryer condenser. Fan 360controller 308 receives inputs or sends outputs from refrigerant-to-airclothes dryer sensor 379F by electrical line 373F, from clothes dryercontrol module 381 F by electrical line 379F, from condensing pressuresensor 377 at accumulator 307 by electrical line 378, from ambient airtemperature sensor 376 at refrigerant-to-air condenser 303 by electricalline 372, and controls fan motor 360 speed with control line 371.Clothes dryer control module 381 tells controller 308 that air heatingis needed and the air conditioning system is turned on by electricalline 374 to in home thermostat 372. Controller 308 then adjusts thespeed of fan 360 per control graphs shown in FIG. 4A and 4B or 5A and 5Bto maintaining the selected air exit temperature from clothes dryercondenser 309F as read at sensor 375F. Note that charts 4A, 4B, 5A and5B are for controlling the water exit temperature and that these waterexit temperatures must be replaced with the wanted clothes dryer airexit temperatures for proper control and operation.

Other applications could be to Pasteurize milk or beer using the wasteheat from a Dairy or Brewery's refrigeration systems or Hospital hotwater heating using the Hospital's air conditioning waste heat. Theseapplications could be met year round as their refrigeration or airconditioning systems run year round. Most air conditioned factory oroffice complexes could have their fluid heating needs met using theirrefrigeration or air conditioning waste heat.

System charging of two condensers in parallel is done with only thecondenser with the larger liquid requirement running. Typically, this isthe refrigerant-to-air condenser 303 in FIG. 3A. However, there areinstances where the other condensers may have the larger liquidrequirement and in those cases, system charging must be done with onlythat condenser running. Charging is complete when the sight glass 319 isfull of liquid.

The size of the accumulator for condensers connected in parallel isdetermined by subtracting the liquid requirements of each condenser whenit alone is running as shown in FIG. 3B and FIG. 3D and plus anadditional safety factor amount such as 1% of the system's liquidrefrigerant volume. For the refrigerant-to-water condenser 334 thevolume is typically equal to ½ of the volume between points 314 a and314 b and the volume between points 314 b and 317 a as shown in FIG. 3D.For the refrigerant-to-air condenser 303, the refrigerant liquid volumeis typically equal to ½ the volume between points 318 a and 318 b andthe volume between points 318 b and 321 a as shown in FIG. 3B.

Referring now to FIG. 4A, a graph is shown of ambient temperaturemeasured at sensor 276 or 376 at the refrigerant-to-air condenser 203 or303 vs. refrigerant-to-air condenser fan speed for maintainingcontrolled exit water temperature from the pool water condenser 202 or302 by controller 208 or 308 in FIG. 2A or FIG. 3A, respectively. Asshown in the previous sentence, the last two digits of an item numberare the same between FIG. 2A and FIG. 3A, and the first digit is either2 or 3, respectively. From this point forward, this convention willapply unless otherwise noted. The graph in FIG. 4A is for an exit watertemperature set point of 120° F. as read by sensor 275 at the pool watercondenser 202 and an operational ambient temperature range from 60 to120° F. as read by sensor 276. The 120° F. exit water temperature setpoint is chosen by the system operator. The operational ambienttemperature range is the expected ambient temperature range at therefrigerant-to-air condenser. As the ambient temperature moves from 60to 120° F., the fan speed will change from zero fan speed to 100% fanspeed with a defined constant exit water temperature from therefrigerant-to-water condenser of 120° F.

Referring now to FIG. 4B, a graph is shown of exit water temperaturefrom the refrigerant-to-water condenser as read at sensor 275 vs.refrigerant-to-air condenser fan speed for maintaining controlled exitwater temperature from the refrigerant-to-water condenser as read atsensor 275. This graph is for the mid point ambient of 90° F. at therefrigerant-to-air condenser as read by sensor 276 and an exit watertemperature from the refrigerant-to-water condenser range of 10° F.centered about the 120 degree set point. As the exit water temperaturefrom the refrigerant-to-water condenser moves from 115 to 125° F., thefan speed control will change from zero fan speed to 100% fan speed at aconstant 90° F. ambient temperature at the refrigerant-to-air condenser.

The control formula for graphs 4A and 4B can be represented by thefollowing mathematical formula:

[25+(T _(ambMP) −T _(amb))K _(amb)]+[25+(T _(wSP) −T _(wact))K _(w)]=%fan speed at the refrigerant-to-air condenser.

Where:

-   All temperatures are in ° F.-   T_(amb) equals the ambient air temperature at the refrigerant-to-air    condenser 276.-   T_(ambMP) equals the mid point of expected ambient air temperatures    at the refrigerant-to-air condenser.-   T_(wact) equals the actual exit water temperature from the    refrigerant-to-water condenser at sensor 275.-   T_(wSP) equals exit water temperature set point desired from the    refrigerant-to-water condenser.-   K_(amb) equals a constant that sets the control sensitivity to    changes in ambient temperature at the refrigerant-to-air condenser.    The ambient air temperature at the refrigerant-to-air condenser has    a second order effect on the actual exit water temperature from the    refrigerant-to-water condenser and Kamb is set at −1.66, a    relatively insensitive number.

K_(w) equals a constant that sets the control sensitivity to changes inexit water temperature from the refrigerant-to-water condenser. Sincecontrolling the exit water temperature from the refrigerant-to-watercondenser is the goal of this control and by definition is the firstorder effect, K_(w) is set at −10 for these graphs. The higher theK_(amb) and K_(w) values, the higher the control reaction to changes intemperature. In the values above, K_(w) is 16.66 times more sensitive toits temperature changes than K_(amb). If the system has problemsmaintaining accurate exit water temperatures from therefrigerant-to-water condenser, Kw should be increased. If Kw is toohigh,-the control will be too sensitive, causing rapid oscillations infan speed. If Kw is too low, the control will be too insensitive,causing problems maintaining accurate exit water temperatures from therefrigerant-to-water condenser. Kw values from −10 to −20 are usuallyacceptable.

The exit water temperature at sensor 275 should run within 2 degrees ofthe T_(wSP) temperature. If the exit water temperature at sensor 275runs to the low side, increase T_(wSP). If, the exit water temperatureat sensor 275 runs to the high side, decrease T_(wSP).

Referring again to FIG. 4A and FIG. 4B, it is possible to change sensor275 or 375 from reading the water exit temperature to reading the systemcondensing temperature and to get similar control results with all otherconditions being the same.

The control formula for graphs 4A and 4B for using system condensingtemperature instead of water exit temperature can be represented by thefollowing mathematical formula:

[25+(T _(ambMP) −T _(amb))K _(amb)]+[25+(T _(conT SP) −T_(conT act))_(KconT)]=% fan speed at the refrigerant-to-air condenser.

Where:

-   All temperatures are in ° F.-   T_(amb) equals the ambient air temperature at the refrigerant-to-air    condenser 276.-   T_(ambMP) equals the mid point of expected ambient air temperatures    at the refrigerant-to-air condenser.-   T_(ConT act) equals the actual system condensing temperature from    the refrigerant-to-water condenser at sensor 275.-   T_(ConT SP) equals system condensing temperature set point need to    produce the desired exit water temperature from the    refrigerant-to-water condenser.-   K_(amb) equals a constant that sets the control sensitivity to    changes in ambient temperature at the refrigerant-to-air condenser.    The ambient air temperature at the refrigerant-to-air condenser has    a second order effect on the actual exit water temperature from the    refrigerant-to-water condenser and K_(amb) is set at −1.66, a    relatively insensitive number.

K_(conT) equals a constant that sets the control sensitivity to changesin system condensing temperature which affects exit water temperature atthe refrigerant-to-water condenser. Since controlling the exit watertemperature from the refrigerant-to-water condenser is the goal of thiscontrol and by definition is the first order effect, K_(conT) is set at−10 for these graphs. The higher the K_(amb) and K_(conT) values, thehigher the control reaction to changes in temperature. In the valuesabove, K_(conT) is 16.66 times more sensitive to its temperature changesthan K_(amb). If the system has problems maintaining accurate exit watertemperatures from the refrigerant-to-water condenser, K_(conT) should beincreased. If K_(conT) is too high, the control will be too sensitive,causing rapid oscillations in fan speed. If K_(conT) is too low, thecontrol will be too insensitive, causing problems maintaining accurateexit water temperatures from the refrigerant-to-water condenser. Kwvalues from −10 to −20 are usually acceptable.

The exit water temperature at sensor 275 should run within 2 degrees ofthe T_(conT SP) depending upon the size of the refrigerant-to-watercondenser. If the exit water temperature at sensor 275 runs to the lowside, increase T_(conT SP). If the exit water temperature at sensor 275runs to the high side, decrease T_(conT SP).

Referring now to FIG. 5A, a graph is shown of ambient temperature at therefrigerant-to-air condenser vs. refrigerant-to-air condenser fan speedfor maintaining controlled exit water temperature from therefrigerant-to-water condenser by controller 208 in FIG. 2A and 308 inFIG. 3A. This graph is for a condensing pressure set point of 253 psiand an operational ambient temperature range from 60 to 120° F. As theambient temperature moves from 60 to 120° F., the fan speed control willchange from zero fan speed to 100% fan speed with a defined constantcondensing pressure of 253 psi.

Referring now to FIG. 5B, a graph is shown of exit water temperaturefrom the refrigerant-to-water condenser vs. condensing for maintainingcontrolled exit water temperature from the refrigerant-to-watercondenser. This graph is for the mid point condensing pressure of 253psi and a condensing pressure range of 6 psi centered about the 253 psiset point. These pressures are for R-22 and must be representative ofthe refrigerant being used by the system. As the condensing pressuremoves from 250 to 256 psi, the fan speed control will change from zerofan speed to 100% fan speed at a constant 90 degree F. ambienttemperature at the refrigerant-to-air condenser.

The control formula for these two graphs can be represented by thefollowing mathematical formula:

[25+(T _(ambMP) −T _(amb))K _(amb)]+[25+(P _(conSP) −P _(act))2.5 K_(con)]=% refrigerant-to-air condenser fan speed.

Where:

-   T_(amb) equals the ambient air temperature at the refrigerant-to-air    condenser.-   T_(ambMP) equals the mid point of expected ambient air temperatures    at the refrigerant-to-air condenser.-   P_(act) equals the actual condensing pressure at the    refrigerant-to-water condenser and is selected based on the    refrigerant used and the desired exit temperature of the    refrigerant-to-water condenser. In this case the pressure is    measured at the accumulator.-   P_(conSP) equals condensing pressure set point desired from the    refrigerant-to-water condenser.-   K_(amb) equals a constant that sets the control sensitivity to    changes in ambient temperature at the refrigerant-to-air condenser.    The ambient air temperature at the refrigerant-to-air( condenser has    a second order effect on the actual exit water temperature from the    refrigerant-to-water condenser and Kamb is set at −1.66, a    relatively insensitive number.

K_(con) equals a constant that sets the control sensitivity to changesin condensing pressure at the refrigerant-to-water condenser and therebythe exit water temperature from the refrigerant-to-water condenser.Since controlling the exit water temperature from therefrigerant-to-water condenser is the goal of this control and bydefinition K_(con) is the first order effect, K_(con) is set at −10 forthese graphs. The higher the K_(amb) and K_(con) values, the higher thecontrol reaction to changes in temperature and pressure, respectively.In the values above, K_(con) is 16.66 times more sensitive to itschanges than K_(amb). If the system has problems maintaining accurateexit water temperatures from the refrigerant-to-water condenser, K_(con)should be increased. If K_(con) is too high, the control will be toosensitive, causing rapid oscillations in fan speed. If Kw is too low,the control will be too insensitive, causing problems maintainingaccurate exit water temperatures from the refrigerant-to-watercondenser. Kw values from −10 to −20 are usually acceptable.

The exit water temperature at sensor 275 should run within 2 degrees ofthe P_(conSP) based on the pressure-temperature of the refrigerant beingused. If the exit water temperature at sensor 275 runs to the low side,increase P_(conSP). If the exit water temperature at sensor 275 runs tothe high side, decrease P_(conSP).

Referring now to FIG. 6A, where Theoretical Outlet Water Temperature,Air Conditioning System Condensing Pressure, Condenser Fan Speed, andHot Water Requirements at various Operational Conditions are shown forFIG. 2A and 3A. Five Operational Conditions are presented. The No. 1Condition is for no pool water heating and the Hot Water requirement iszero. The air conditioning system is working normally as shown in FIG.2B or FIG. 3B and the refrigerant-to-air fan motor 260 is running at100%. The No. 5 Condition is for full pool water heating and the HotWater requirement is 100%. Refrigerant condensing is taking place onlyin the refrigerant-to-water condenser as shown in FIG. 2D and 3D and therefrigerant-to-air fan motor 250 is not running, forcing all condensingto take place at the refrigerant-to-water condenser 234. The No. 2, No.3, and No. 4 conditions are for 25%, 50% and 75% Hot Water requirements.Fan motor 260 is controlled by controller 208 per control graphs 4A and4B or 5A and 5B. The ambient air temperature at sensor 276 is 90° F. andhas the fan motor 260 running at 50%. Sensor 275 gives the exittemperature of the heated pool water and controller 208 reads thissensor and adjusts fan 260 speed up or down from the 50% level set byambient sensor 275 per the control formula given previously or controlgraphs in FIG. 4A and 4B. Since the control formula is 16.66 times moresensitive to the exit water temperature than the ambient airtemperature, slight changes in exit water temperature will be correctedby significant changes in refrigerant-to-air condenser fan speedallowing consistent water temperature control over a wide range ofoperating conditions.

The same results can be reached by replacing Sensor 275 or 375 readingswith condenser pressure sensor 277 or 377 and using control graphs shownin FIG. 5 a and 5B and their formula presented previously.

While the invention has been particularly shown and described withreference to preferred embodiments thereof it is well understood bythose skilled in the art that various changes and modifications can bemade in the invention without departing from the spirit and scope of theinvention as defined by the appended claims.

1. A heat pump system for refrigeration or air conditioning, and forheating a fluid comprising: a compressor for supplying high pressure,high temperature gaseous refrigerant to a first condenser for heatexchange with a first condensing fluid and to a second condenser forheat exchange with a second condensing fluid; an expansion valve forreceiving high pressure liquid refrigerant from said first and saidsecond condensers; an evaporator for receiving low pressure liquidrefrigerant from said expansion valve and supplying low pressure gaseousrefrigerant to said compressor; a controller for adjusting thecondensing fluid flow rate of said second condenser based on inputs froma first sensor for reading the condensing fluid condition at the firstcondenser and from a second sensor reading the ambient condition of thesecond condensing fluid.
 2. The system of claim 1 wherein said firstcondenser and said second condenser are connected in parallel.
 3. Thesystem of claim 2 wherein an accumulator is connected between said firstand said second condensers for receiving gaseous and or liquidrefrigerant, and said accumulator supplies liquid refrigerant to saidexpansion valve.
 4. The system of claim 1 wherein said first condenserand said second condenser are connected in series, and an accumulator isconnected between said second condenser and said expansion valve, and apressure equalization line is connected between said compressor and saidaccumulator, and said accumulator supplies liquid refrigerant to saidexpansion valve.
 5. The system of claim 1 wherein said first sensorreads the condensing fluid exit temperature of said first condenser, andsaid second sensor reads the ambient air temperature at said secondcondenser, and said second condensing fluid is ambient air.
 6. Thesystem of claim 5 wherein said controller adjusts the ambient air flowas a percentage of maximum flow in accordance with the followingformula: [25+(T_(ambMP)−T_(amb))K_(amb)]+[25+(T_(wSP)−T_(w))K_(w)]. 7.The system of claim 6 wherein said ambient air flow rate at said secondcondenser is adjusted by changing the ambient air fan speed of saidsecond condenser.
 8. The system of claim 1 wherein said first sensorreads the condensing pressure of said refrigeration or air conditioningsystem, and said second sensor reads the ambient air temperature at saidsecond condenser, and said second condensing fluid is ambient air. 9.The system of claim 8 wherein said controller adjusts the ambient airflow rate as a percentage of maximum flow rate in accordance with thefollowing formula:[25+(T_(ambMP)−T_(amb))K_(amb)]+[25+(P_(conSP)−P_(act))2.5 K_(con)]. 10.The system of claim 9 wherein said ambient air flow rate at said secondcondenser is adjusted by changing the ambient air fan speed of saidsecond condenser.
 11. The system of claim 1 wherein said first sensorreads the condensing temperature of said refrigeration or airconditioning system, and said second sensor reads the ambient airtemperature at said second condenser, and said second condensing fluidis ambient air.
 12. The system of claim 11 wherein said controlleradjusts the ambient air flow as a percentage of maximum flow inaccordance with the following formula:[25+(T_(ambMP)−T_(amb))K_(amb)]+[25+(T_(conT SP)−T_(conT))K_(conT)]. 13.The system of claim 12 wherein said ambient air flow rate at said secondcondenser is adjusted by changing the ambient air fan speed of saidsecond condenser.
 14. A heat pump system for refrigeration or airconditioning, and for heating a fluid comprising: a compressor forsupplying high pressure, high temperature gaseous refrigerant to a firstcondenser for heat exchange with a first condensing fluid and to asecond condenser for heat exchange with a second condensing fluid; saidfirst and second condensers being connected in parallel; an accumulatorfor receiving high pressure gaseous and/or liquid refrigerant from saidfirst and second condensers: an expansion valve for receiving highpressure liquid refrigerant from said accumulator; an evaporator forreceiving low pressure liquid refrigerant from said expansion valve andsupplying low pressure gaseous refrigerant to said compressor; acontroller for adjusting the condensing fluid flow rate of said secondcondenser based on inputs from a first sensor for reading the condensingfluid condition at the first condenser and from a second sensor readingthe ambient condition of the second condensing fluid.
 15. A heat pumpsystem for refrigeration or air conditioning, and heating a fluidcomprising: a compressor supplying high pressure, high temperaturegaseous refrigerant to a first condenser for heat exchange with a firstcondensing fluid; said first condenser supplying gaseous and/or liquidrefrigerant to a second condenser for heat exchange with a secondcondenser fluid; an accumulator for receiving high pressure liquidrefrigerant from said second condenser; a pressure equalization linebetween said compressor and said accumulator: an expansion valve forreceiving high pressure liquid refrigerant from said accumulator; anevaporator for receiving low pressure liquid refrigerant from saidexpansion valve and supplying low pressure gaseous refrigerant to saidcompressor; a controller for adjusting the condensing fluid flow rate ofsaid second condenser based on inputs from a first sensor for readingthe condensing fluid condition at the first condenser and from a secondsensor reading the ambient condition of the second condensing fluid. 16.The system of claim 1 where said first fluid is selected from but notlimited to water, milk, beer, oil, or air, and said second fluid isselected from but not limited to air, water, oil, or a water antifreezemix.
 17. The system of claim 14 where said first fluid is selected frombut not limited to water, milk, beer, oil, or air, and said second fluidis selected from but not limited to air, water, oil, or a waterantifreeze mix.